JP2009264404A - Sealed rolling bearing unit and seal ring - Google Patents

Sealed rolling bearing unit and seal ring Download PDF

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Publication number
JP2009264404A
JP2009264404A JP2008111173A JP2008111173A JP2009264404A JP 2009264404 A JP2009264404 A JP 2009264404A JP 2008111173 A JP2008111173 A JP 2008111173A JP 2008111173 A JP2008111173 A JP 2008111173A JP 2009264404 A JP2009264404 A JP 2009264404A
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Prior art keywords
seal
ring
inner ring
peripheral surface
seal ring
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JP2008111173A
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Japanese (ja)
Inventor
Yohei Kashiwakura
洋平 柏倉
Hiroki Sakaguchi
裕樹 坂口
Seisuke Takeda
精介 竹田
Yasushi Amano
靖 天野
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NSK Ltd
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NSK Ltd
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Priority to JP2008111173A priority Critical patent/JP2009264404A/en
Publication of JP2009264404A publication Critical patent/JP2009264404A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/768—Sealings of ball or roller bearings between relatively stationary parts, i.e. static seals
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/60—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/38—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers
    • F16C19/383—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F16C19/388—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with four rows, i.e. four row tapered roller bearings

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To obtain a structure capable of preventing the occurrence of a pressure difference between a rolling element arranging space 16 and an external space, even if the bearing temperature changes, in the structure for fluid-tightly blocking up mutual end surfaces in the axial direction of both inner ring elements 11 and 11 by a seal ring 7 installed in a recessed groove 18, by forming the recessed groove 18 on an inner peripheral surface of a butting part of the mutual end surfaces in the axial direction of a pair of inner ring elements 11 and 11. <P>SOLUTION: The seal ring 7 is constituted by combining an annular ring-shaped sealant and an annular ring-shaped or segmental annular ring-shaped core material for reinforcing the sealant. Among these, the sealant is made of a water repellent-oil repellent, ventilating and flexible raw material. In a state of installing the seal ring 7 in the recessed groove 18, the sealant is respectively contacted at an interference over the whole periphery with both sidewall surfaces in at least the axial direction among an inner surface of the recessed groove 18. The problem is solved by adopting such a constitution. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

この発明は、例えば圧延機を構成するロールの両端部に設けたロールネックを支持装置に対して回転自在に支持する為に使用する密封型転がり軸受ユニットと、この密封型転がり軸受ユニットの転動体設置空間を密封する為に使用するシール環との改良に関する。   The present invention relates to, for example, a sealed rolling bearing unit used for rotatably supporting roll necks provided at both ends of a roll constituting a rolling mill with respect to a support device, and a rolling element of the sealed rolling bearing unit. The present invention relates to an improvement with a seal ring used for sealing an installation space.

金属材料に圧延加工を施す為の、圧延機を構成するロールは、軸方向両端面の中心部に設けたロールネックと呼ばれる円柱部を固定の支持装置に対し、例えば図１４に示す様な密封型多列円すいころ軸受により回転自在に支持している。この図１４に示した密封型多列円すいころ軸受は、特許文献１に記載されたもので、外輪１と、内輪２と、複数個の円すいころ３、３と、１対の円環状のシールホルダ４、４と、１対の摺接型のシールリング５、５と、１対のＯリング６、６と、１個のシール環７とを備える。   A roll constituting a rolling mill for rolling a metal material is sealed as shown in FIG. 14, for example, with respect to a support device that fixes a cylindrical portion called a roll neck provided at the center of both axial end faces. It is rotatably supported by type multi-row tapered roller bearings. The sealed multi-row tapered roller bearing shown in FIG. 14 is described in Patent Document 1, and includes an outer ring 1, an inner ring 2, a plurality of tapered rollers 3, 3, and a pair of annular seals. Holders 4, 4, a pair of sliding contact type seal rings 5, 5, a pair of O-rings 6, 6, and one seal ring 7 are provided.

このうちの外輪１は、軸方向中央部に配置した１個の外輪素子８ａと、軸方向両端部に配置した２個の外輪素子８ｂ、８ｂと、軸方向に関して隣り合う、これら各外輪素子８ａ、８ｂ同士の間に挟持する状態で設けた、それぞれが短円筒状である２個の外輪間座９、９とから成る。上記軸方向中央部に配置した１個の外輪素子８ａの内周面には、それぞれが部分円すい凹面状の外輪軌道１０、１０を、２列形成している。又、上記軸方向両端部に配置した２個の外輪素子８ｂ、８ｂの内周面にはそれぞれ、部分円すい凹面状の外輪軌道１０を、１列ずつ形成している。従って、上記外輪１の内周面には、４列の外輪軌道１０、１０が設けられている。   Of these, the outer ring 1 includes one outer ring element 8a disposed in the central portion in the axial direction and two outer ring elements 8b and 8b disposed at both ends in the axial direction, which are adjacent to each other in the axial direction. , 8b, and two outer ring spacers 9, 9 each having a short cylindrical shape. Two rows of outer ring raceways 10 and 10 each having a conical concave shape are formed on the inner peripheral surface of one outer ring element 8a arranged in the central portion in the axial direction. Further, the outer ring raceway 10 having a partially conical concave shape is formed in each row on the inner peripheral surface of the two outer ring elements 8b, 8b arranged at both ends in the axial direction. Therefore, four rows of outer ring raceways 10 and 10 are provided on the inner peripheral surface of the outer ring 1.

又、上記内輪２は、互いの軸方向端面同士を突き当てた、１対の内輪素子１１、１１から成る。これら両内輪素子１１、１１の外周面にはそれぞれ、部分円すい凸面状の内輪軌道１２、１２を、２列ずつ形成している。従って、上記内輪２の外周面には、４列の内輪軌道１２、１２が設けられている。又、上記各円すいころ３、３は、上記４列の外輪軌道１０、１０と上記４列の内輪軌道１２、１２との間に、各列毎に複数個ずつ、保持器１３、１３により保持した状態で転動自在に設けられている。   The inner ring 2 is composed of a pair of inner ring elements 11, 11 that face each other in the axial direction. Two inner ring raceways 12 and 12 having a partially conical convex shape are formed on the outer peripheral surfaces of both inner ring elements 11 and 11 respectively. Therefore, four rows of inner ring raceways 12 and 12 are provided on the outer peripheral surface of the inner ring 2. The tapered rollers 3 and 3 are held by the cages 13 and 13 between the four rows of outer ring raceways 10 and 10 and the four rows of inner ring raceways 12 and 12, respectively. It is provided so that it can roll freely.

又、上記１対の円環状のシールホルダ４、４は、上記外輪１の軸方向両側に隣接配置している。そして、これら両シールホルダ４、４の内周面と、上記内輪２の軸方向両端部外周面との間に、それぞれ上記両シールリング５、５を組み付けている。これら両シールリング５、５はそれぞれ、円環状の芯金１４と、この芯金１４の内周縁部分に全周に亙り結合固定した円環状の弾性材１５とを備える。そして、このうちの芯金１４を上記両シールホルダ４、４に内嵌固定すると共に、上記弾性材１５の先端縁を、上記内輪２の軸方向両端部外周面に摺接させている。これにより、上記外輪１の内周面と上記内輪２の外周面との間に存在する、転動体設置空間１６の軸方向両端開口を密閉している。又、上記両シールホルダ４、４の外周面には、それぞれ係止溝１７、１７を全周に亙り形成すると共に、これら各係止溝１７、１７内に前記各Ｏリング６、６を係止している。自由状態で、これら各Ｏリング６、６の外径寸法は、上記各シールホルダ４、４の外径寸法よりも大きくなっている。   The pair of annular seal holders 4, 4 are disposed adjacent to both sides in the axial direction of the outer ring 1. The seal rings 5 and 5 are assembled between the inner peripheral surfaces of the seal holders 4 and 4 and the outer peripheral surfaces of both end portions of the inner ring 2 in the axial direction. Each of the seal rings 5 and 5 includes an annular cored bar 14 and an annular elastic member 15 that is coupled and fixed to the inner peripheral edge of the cored bar 14 over the entire circumference. Of these, the metal core 14 is fitted and fixed to the seal holders 4 and 4, and the leading edge of the elastic material 15 is brought into sliding contact with the outer peripheral surfaces of both end portions in the axial direction of the inner ring 2. Thereby, both axial direction opening of the rolling element installation space 16 which exists between the inner peripheral surface of the said outer ring | wheel 1 and the outer peripheral surface of the said inner ring | wheel 2 is sealed. Further, locking grooves 17 and 17 are formed on the outer peripheral surfaces of the seal holders 4 and 4 over the entire circumference, and the O-rings 6 and 6 are engaged in the locking grooves 17 and 17. It has stopped. In a free state, the outer diameter dimensions of the O-rings 6 and 6 are larger than the outer diameter dimensions of the seal holders 4 and 4.

又、上記両内輪素子１１、１１の軸方向端面同士の突き当て部の内周面には、これら両内輪素子１１、１１同士の間に掛け渡す状態で凹溝１８を、全周に亙り形成している。そして、この凹溝１８内に、前記シール環７を組み付けている。図１５に詳示する様に、このシール環７は、ゴムにより全体を円環状に形成したシール材１９と、このシール材１９を補強する為の、金属製で円環状の芯材２２とから成る。このうちのシール材１９は、断面略矩形で全体を円環状に形成した基部２３と、この基部２３の全周から軸方向に延出する状態で形成された、径方向の肉厚が比較的小さい円環状のシールリップ２４とを備える。この様なシール環７は、図示の様に凹溝１８内に組み付けた状態で、上記シール材１９を構成する基部２３を、この凹溝１８の底面及び軸方向両側壁面のうち、一方（図１５の左方）の内輪素子１１に対応する部分の全周に弾性的に接触させている。これと共に、上記シール材１９を構成するシールリップ２４の先端縁を、上記凹溝１８の軸方向両側壁面のうち、他方（図１５の右方）の内輪素子１１に対応する部分の全周に弾性的に接触させている。これにより、上記両内輪素子１１、１１の軸方向端面同士の間を密閉している。   In addition, a concave groove 18 is formed on the inner peripheral surface of the abutting portion between the axial end surfaces of the inner ring elements 11, 11 so as to extend between the inner ring elements 11, 11. is doing. The seal ring 7 is assembled in the groove 18. As shown in detail in FIG. 15, the seal ring 7 is composed of a seal material 19 formed entirely in an annular shape with rubber, and a metal and annular core material 22 for reinforcing the seal material 19. Become. Of these, the sealing member 19 has a base portion 23 that is substantially rectangular in cross section and formed in an annular shape as a whole, and a radial thickness formed in a state extending in the axial direction from the entire circumference of the base portion 23. And a small annular seal lip 24. Such a seal ring 7 is assembled in the groove 18 as shown in the figure, and the base 23 constituting the seal material 19 is placed on one of the bottom surface and both axial side walls of the groove 18 (see FIG. 15) is elastically brought into contact with the entire circumference of the portion corresponding to the inner ring element 11. At the same time, the tip edge of the seal lip 24 constituting the seal material 19 is placed on the entire circumference of the portion corresponding to the inner ring element 11 on the other side (right side in FIG. 15) of both side walls in the axial direction of the groove 18. It is in elastic contact. Thereby, the space between the axial end surfaces of the inner ring elements 11 and 11 is sealed.

上述の様に構成する密封型多列円すいころ軸受ユニットにより、圧延機を構成するロールの軸方向端面の中心部に設けた円柱状のロールネック（図示せず）を、支持装置を構成するハウジング（図示せず）の内径側に回転自在に支持する場合には、このハウジングに上記外輪１及び１対のシールホルダ４、４を内嵌支持すると共に、上記ロールネックに上記内輪２を外嵌支持する。又、これに伴い、上記各シールホルダ４、４の外周面に形成した係止溝１７、１７の底面と、上記ハウジングの円筒状の内周面との間で、上記各Ｏリング６、６を弾性的に圧縮する。これにより、上記各シールホルダ４、４の外周面と上記ハウジングの内周面との間を密閉する。   A cylindrical roll neck (not shown) provided at the center of the axial end surface of the roll constituting the rolling mill by the sealed multi-row tapered roller bearing unit configured as described above is a housing constituting the support device. When the inner ring side (not shown) is rotatably supported, the outer ring 1 and the pair of seal holders 4 and 4 are fitted and supported on the housing, and the inner ring 2 is fitted on the roll neck. To support. Accordingly, the O-rings 6, 6 are provided between the bottom surfaces of the locking grooves 17, 17 formed on the outer peripheral surfaces of the seal holders 4, 4 and the cylindrical inner peripheral surface of the housing. Is elastically compressed. Thereby, the space between the outer peripheral surface of each of the seal holders 4 and 4 and the inner peripheral surface of the housing is sealed.

上述の様な密封型多列円すいころ軸受ユニットは、外部に冷却水や塵芥等の異物が存在する環境下で使用される。又、上述の様な密封型多列円すいころ軸受ユニットの場合、メンテナンス時等の交換性を考慮し、上記ロールネックの外周面と上記内輪２の内周面との嵌め合いは、隙間嵌め（ルーズフィット）にしている。この為、これら両周面同士の間で滑りが起こり、摩耗粉が発生する。従って、これら冷却水、塵芥等の異物、摩耗粉が存在する外部空間と、前記転動体設置空間１６との間に存在する複数の連通路を、それぞれ前記１対のシールリング５、５と、上記１対のＯリング６、６と、上記１個のシール環７とにより塞ぐ事で、上記転動体設置空間１６を密封している。そして、この様な構成を採用する事により、上記外部空間から上記転動体設置空間１６内に上記冷却水等が入り込む事を防止すると共に、この転動体設置空間１６内に封入した潤滑用のグリースが上記外部空間に漏洩する事を防止している。   The sealed multi-row tapered roller bearing unit as described above is used in an environment where foreign matters such as cooling water and dust are present outside. Further, in the case of the sealed multi-row tapered roller bearing unit as described above, the fit between the outer peripheral surface of the roll neck and the inner peripheral surface of the inner ring 2 is a clearance fit ( Loose fit). For this reason, slip occurs between the two peripheral surfaces, and wear powder is generated. Therefore, a plurality of communication paths existing between the external space in which foreign matter such as cooling water, dust and the like, wear powder exists, and the rolling element installation space 16 are respectively connected to the pair of seal rings 5 and 5. The rolling element installation space 16 is sealed by closing with the pair of O-rings 6 and 6 and the single seal ring 7. Further, by adopting such a configuration, the cooling water or the like is prevented from entering the rolling element installation space 16 from the external space, and the lubricating grease sealed in the rolling element installation space 16 Is prevented from leaking into the external space.

ところで、上述したロールネック用の密封型多列円すいころ軸受ユニットの場合、運転時に高温になる事で、上記転動体設置空間１６内の空気が膨張すると、この転動体設置空間１６内の空気が、上記１対のシールリング５、５を構成する弾性材１５、１５の先端縁と上記内輪２の軸方向両端部外周面との摺接部（間部分）や、上記シール環７を構成するシールリップ２４の先端縁と上記凹部１８の内面との接触部（間部分）を通じて、外部空間に徐々に漏れ出す。尚、上述した従来構造の第１例の場合には、上記内輪２の軸方向両端部外周面に摺接する上記両弾性材１５、１５の先端縁と、上記凹部１８の内面に接触する上記シールリップ２４の先端縁とが、それぞれ外部空間側に向いて傾斜している。即ち、上記各摺接部及び上記接触部を通じて、上記転動体設置空間１６内の空気が外部空間に漏れ出す傾向となった場合に、上記各摺接部及び上記接触部の一部に隙間が生じ易くなっている。この為、上記空気の漏れ出しは、容易に行われる。   By the way, in the case of the above-described sealed multi-row tapered roller bearing unit for the roll neck, when the air in the rolling element installation space 16 expands due to a high temperature during operation, the air in the rolling element installation space 16 A sliding contact portion (intersection) between the tip edges of the elastic members 15 and 15 constituting the pair of seal rings 5 and 5 and the outer peripheral surfaces of both end portions in the axial direction of the inner ring 2 and the seal ring 7 are constituted. Through the contact portion (intermediate portion) between the tip edge of the seal lip 24 and the inner surface of the concave portion 18, it gradually leaks into the external space. In the case of the first example of the above-described conventional structure, the seals that are in contact with the tip edges of the elastic members 15 and 15 that are in sliding contact with the outer peripheral surfaces of both ends in the axial direction of the inner ring 2 and the inner surfaces of the recesses 18. The tip edge of the lip 24 is inclined toward the outer space side. That is, when the air in the rolling element installation space 16 tends to leak into the external space through each sliding contact portion and the contact portion, there is a gap in each sliding contact portion and part of the contact portion. It tends to occur. For this reason, the leakage of the air is easily performed.

一方、その後、運転を停止して低温になる事で、上記転動体設置空間１６内の空気が収縮すると、上記各摺接部及び上記接触部を通じて、外部空間の空気が上記転動体設置空間１６内に吸い込まれる傾向となる。ところが、上述した従来構造の第１例の場合には、上記内輪２の軸方向両端部外周面に摺接する上記両弾性材１５、１５の先端縁と、上記凹部１８の内面に接触する上記シールリップ２４の先端縁とが、それぞれ外部空間側に向いて傾斜している。即ち、上記各摺接部や上記接触部を通じて、外部空間に存在する空気が上記転動体設置空間１６内に吸い込まれる傾向となった場合に、上記各摺接部及び上記接触部の一部に隙間が生じにくくなっている。この為、上記空気の吸い込みが殆ど行われず、上記転動体設置空間１６が負圧状態となる。そして、この様に転動体設置空間１６が負圧状態となる結果、著しい場合には、上記各摺接部及び上記接触部を通じて、外部空間から上記転動体設置空間１６内に上記冷却水が吸い込まれると言った不具合が発生する可能性があった。又、上記転動体設置空間１６が負圧状態になると、外部空間の大気圧によって、上記両シールリング５、５を構成する弾性材１５、１５の先端縁が、上記内輪２の軸方向両端部外周面に強く押し付けられる。この結果、これら両弾性材１５、１５の先端縁の摩耗が促進され、これら両弾性材１５、１５のシール機能の低下速度が高まる。従って、その分だけ、上記冷却水が上記両摺接部を通じて上記転動体設置空間１６内に、より引き込まれ易くなる。   On the other hand, when the air in the rolling element installation space 16 contracts after the operation is stopped and the temperature is lowered, the air in the external space is passed through the sliding contact part and the contact part. It tends to be sucked in. However, in the case of the first example of the conventional structure described above, the seals that contact the tip edges of the elastic members 15 and 15 that are in sliding contact with the outer peripheral surfaces of both axial ends of the inner ring 2 and the inner surfaces of the recesses 18. The tip edge of the lip 24 is inclined toward the outer space side. That is, when the air existing in the external space tends to be sucked into the rolling element installation space 16 through each sliding contact portion or the contact portion, the sliding contact portion and a part of the contact portion are provided. The gap is less likely to occur. Therefore, the air is hardly sucked, and the rolling element installation space 16 is in a negative pressure state. As a result of the negative pressure state of the rolling element installation space 16 as described above, the cooling water is sucked into the rolling element installation space 16 from the external space through each sliding contact part and the contact part. There was a possibility that a problem that occurred. Further, when the rolling element installation space 16 is in a negative pressure state, the leading edges of the elastic members 15 and 15 constituting the both seal rings 5 and 5 are caused by the atmospheric pressure of the outer space so that both ends of the inner ring 2 in the axial direction. Strongly pressed against the outer peripheral surface. As a result, the wear of the leading edges of both elastic members 15 and 15 is promoted, and the rate of decrease in the sealing function of both elastic members 15 and 15 is increased. Therefore, the cooling water is more easily drawn into the rolling element installation space 16 through the sliding contact portions.

上記冷却水が上記転動体設置空間１６内に引き込まれると、この転動体設置空間１６に存在するグリースの潤滑性能が損なわれ、軸受寿命が低下する。従って、この様な事態が発生するのを回避すべく、上記冷却水が上記両摺接部を通じて上記転動体設置空間１６内に引き込まれる事を、有効に防止する必要がある。この為に具体的には、上記転動体設置空間１６が負圧状態となる事を防止できる構造を実現する必要がある。   When the cooling water is drawn into the rolling element installation space 16, the lubrication performance of the grease existing in the rolling element installation space 16 is impaired, and the bearing life is reduced. Therefore, in order to avoid such a situation, it is necessary to effectively prevent the cooling water from being drawn into the rolling element installation space 16 through the sliding contact portions. Therefore, specifically, it is necessary to realize a structure capable of preventing the rolling element installation space 16 from becoming a negative pressure state.

この様な事情に鑑みて、特許文献２には、上述の図１５に示したシール環７に代えて、図１６に示す様なシール環７ａを使用する構造が記載されている。この図１６に示した従来構造の第２例を構成するシール環７ａは、ゴムにより全体を円環状に形成したシール材１９ａと、このシール材１９ａの内周面の幅方向中央部に全周に亙り形成した係止溝２０内に係止した、芯材である円環状スプリング２１とを備える。そして、このうちのシール材１９ａ（図１６では便宜上、自由状態で示している。）の一部を、上記凹溝１８の底面の幅方向両側部分及び両側壁面に全周に亙り接触させている。これと共に、上記円環状スプリング２１の弾力により、上記シール材１９ａを上記凹溝１８の底面に向け、径方向外方に付勢している。そして、この様な構成を採用する事により、上記シール環７ａによって、１対の内輪素子１１、１１の軸方向端面同士の間を密閉している。これと共に、上記凹溝１８の内面に対する上記シール材１９ａの締め代、並びに、上記円環状スプリング２１の弾力を適度に調節する事により、高温時及び低温時にそれぞれ、上記凹溝１８の内面と上記シール材１９ａとの接触部を通じて、転動体設置空間１６（図１４参照）と外部空間との間で空気のみが出入りできる様にし、その他の異物等が出入りするのを防止できる様にしている。   In view of such circumstances, Patent Document 2 describes a structure in which a seal ring 7a as shown in FIG. 16 is used instead of the seal ring 7 shown in FIG. The seal ring 7a that constitutes the second example of the conventional structure shown in FIG. 16 includes a seal material 19a that is formed into a ring shape entirely from rubber, and an entire circumference in the center in the width direction of the inner peripheral surface of the seal material 19a. And an annular spring 21 serving as a core material, which is locked in a locking groove 20 formed over the surface. A part of the sealing material 19a (shown in a free state for convenience in FIG. 16) is brought into contact with the entire circumference of both sides and both side walls of the bottom surface of the concave groove 18 in the width direction. . At the same time, the elastic force of the annular spring 21 urges the sealing material 19a toward the bottom surface of the concave groove 18 outward in the radial direction. And by employ | adopting such a structure, between the axial direction end surfaces of a pair of inner ring elements 11 and 11 is sealed with the said seal ring 7a. At the same time, by appropriately adjusting the tightening margin of the sealing material 19a with respect to the inner surface of the concave groove 18 and the elasticity of the annular spring 21, the inner surface of the concave groove 18 and the above-mentioned at high temperature and low temperature respectively. Through the contact portion with the sealing material 19a, only air can enter and exit between the rolling element installation space 16 (see FIG. 14) and the external space, and other foreign matters can be prevented from entering and exiting.

この様な従来構造の第２例によれば、上記転動体設置空間１６が負圧状態になる事を有効に防止できる為、上述の従来構造の第１例で説明した様な不具合が発生する事を有効に防止できる。ところが、上述の様な従来構造の第２例の場合には、上記凹溝１８の内面に対する上記シール材１９ａの締め代、並びに、上記円環状スプリング２１の弾力を適度に調節する事が困難であり、この適度な調整を実現する為に高精度な寸法管理等が必要になる為、製造コストが嵩むと言った問題がある。尚、この調整によって、上記締め代及び弾力が小さくなり過ぎると、上記接触部を通じて外部空間から上記転動体設置空間１６内に異物等が入り込み易くなったり、或いは、上記シール環７ａの一部が径方向内方に垂れ下がって上記凹溝１８外に突出し、メンテナンス時に内輪２の内径側からロールネックを抜き差しする際に、当該突出した部分がこのロールネックに干渉して破損すると言った不具合が発生する。反対に、上記締め代及び弾力が大きくなり過ぎると、低温時の通気性を失って、上述した従来構造の第１例の場合と同様の不具合が発生する。   According to the second example of such a conventional structure, it is possible to effectively prevent the rolling element installation space 16 from being in a negative pressure state, so that the problem described in the first example of the conventional structure described above occurs. Things can be effectively prevented. However, in the case of the second example of the conventional structure as described above, it is difficult to properly adjust the tightening margin of the sealing material 19a against the inner surface of the concave groove 18 and the elasticity of the annular spring 21. In addition, there is a problem that the manufacturing cost increases because highly accurate dimensional management or the like is necessary to realize this appropriate adjustment. In addition, if the tightening allowance and the elasticity are too small due to this adjustment, foreign matter or the like easily enters the rolling element installation space 16 from the external space through the contact portion, or a part of the seal ring 7a is formed. When the roll neck hangs inward in the radial direction and protrudes out of the concave groove 18, and the roll neck is inserted and removed from the inner diameter side of the inner ring 2 during maintenance, the protruding portion interferes with the roll neck and breaks. To do. On the other hand, if the tightening allowance and elasticity are too large, the air permeability at low temperatures is lost and the same problem as in the first example of the conventional structure described above occurs.

又、前記特許文献１には、上述した従来構造の第１例の改良品として、図１７に示す様な構造が記載されている。この図１７に示した従来構造の第３例の場合には、シール環７′のシール材１９′を構成するシールリップ２４の軸方向中間部の円周方向複数個所に、それぞれ円形の薄肉部２５を形成すると共に、これら各薄肉部２５にそれぞれ、これら各薄肉部２５を１対の半円形部分に２分割する、直径方向に亙る切れ目２６を形成している。自由状態で、これら各切れ目２６部分は、それぞれ閉じた状態になっている。この様に構成する従来構造の第３例の場合には、温度変化に伴って転動体設置空間１６（図１４参照）と外部空間との間に所定の圧力差が生じた場合に、次の様な圧力差の調整機能が働く。即ち、上記両空間同士の間の圧力差が所定値に達すると、この圧力差によって、上記各切れ目２６部分が弾性的に広がる。そして、これら各切れ目２６部分を通じて、上記両空間同士の間で空気が出入する事により、上記圧力差が上記所定値以下に抑えられる。この為、上記転動体設置空間１６が過度な負圧状態になる事を有効に防止できる。従って、上述の従来構造の第１例で説明した不具合が発生する事を有効に防止できる。   Further, Patent Document 1 describes a structure as shown in FIG. 17 as an improved product of the first example of the conventional structure described above. In the case of the third example of the conventional structure shown in FIG. 17, circular thin-walled portions are respectively provided at a plurality of locations in the circumferential direction of the axially intermediate portion of the seal lip 24 constituting the seal material 19 'of the seal ring 7'. 25, and each thin portion 25 is formed with a cut 26 extending in the diametrical direction, which divides each thin portion 25 into a pair of semicircular portions. In the free state, each of the cut portions 26 is in a closed state. In the case of the third example of the conventional structure configured as described above, when a predetermined pressure difference is generated between the rolling element installation space 16 (see FIG. 14) and the external space as the temperature changes, Various pressure differential adjustment functions work. That is, when the pressure difference between the two spaces reaches a predetermined value, each of the cut portions 26 is elastically spread by the pressure difference. Then, air enters and exits between the two spaces through each of the cuts 26, whereby the pressure difference is suppressed to the predetermined value or less. For this reason, it can prevent effectively that the said rolling-element installation space 16 becomes an excessive negative pressure state. Therefore, it is possible to effectively prevent the occurrence of the problems described in the first example of the conventional structure described above.

ところが、この様な従来構造の第３例の場合には、上記シールリップ２４の加工が面倒でコストが嵩む。しかも、上記切れ目２６部分の開閉を適切に行わせて、上述した圧力差の調整機能を的確に発揮させる為には、凹溝１８の内面に対する上記シールリップ２４の締め代を適正に管理して、上記切れ目２６部分の応力を適正にしておく必要がある。この為に具体的には、上記凹溝１８、並びに、上記シールリップ２４を含んで構成するシール材１９′の寸法精度及び形状精度を、それぞれ十分に確保する必要がある。従って、その分だけ、上記凹溝１８を形成する１対の内輪素子１１、１１の加工コスト、並びに、上記シール材１９′を造る為の成形型のコストが嵩む。   However, in the case of the third example having such a conventional structure, the processing of the seal lip 24 is cumbersome and costly. In addition, in order to appropriately open and close the cut portion 26 and to exert the above-described pressure difference adjustment function appropriately, the tightening margin of the seal lip 24 with respect to the inner surface of the groove 18 is appropriately managed. It is necessary to make the stress of the cut portion 26 appropriate. For this purpose, it is necessary to sufficiently secure the dimensional accuracy and shape accuracy of the sealing material 19 ′ including the concave groove 18 and the sealing lip 24. Accordingly, the machining cost of the pair of inner ring elements 11 and 11 forming the concave groove 18 and the cost of the mold for producing the sealing material 19 ′ are increased accordingly.

特開２０００−１０４７４７号公報JP 2000-104747 A 特開平９−３２９２４３号公報Japanese Patent Laid-Open No. 9-329243

本発明の密封型転がり軸受ユニット及びシール環は、上述の様な事情に鑑み、温度変化が生じる状況で、１対の内輪素子の軸方向端面同士の間の液密を保持できると共に、転動体設置空間と外部空間との間の圧力差をなくす事ができ、しかも凹溝を形成する上記各内輪素子の加工コスト、並びに、この凹溝内に組み付けるシール環の製造コストを抑えられる構造を実現すべく発明したものである。   The sealed-type rolling bearing unit and seal ring of the present invention are capable of maintaining liquid-tightness between the axial end faces of a pair of inner ring elements in a situation where temperature changes occur in view of the above-described circumstances, and rolling elements Realizes a structure that can eliminate the pressure difference between the installation space and the external space, and can reduce the processing cost of each inner ring element that forms the groove and the manufacturing cost of the seal ring to be assembled in the groove. Invented as much as possible.

本発明の対象となる密封型転がり軸受ユニットは、内周面に複列又は多列の外輪軌道を有する外輪と、外周面に複列又は多列の内輪軌道を有する内輪と、これら各外輪軌道とこれら各内輪軌道との間に、各列毎に複数個ずつ、転動自在に設けられた転動体と、上記外輪の内周面と上記内輪の外周面との間に存在する転動体設置空間の軸方向両端開口を塞ぐ、１対の摺接型のシールリングとを備える。又、上記内輪は、それぞれがその外周面に上記内輪軌道を１列以上有し、且つ、互いの軸方向端面同士を突き当てた１対の内輪素子を含んで構成している。又、これら両内輪素子の軸方向端面同士の突き当て部の内周面又は外周面に凹溝を、これら両内輪素子に掛け渡す状態で全周に亙り形成している。又、この凹溝内に、上記両内輪素子の軸方向端面同士の間を液密に塞ぐシール環を組み付けている。   A sealed rolling bearing unit that is an object of the present invention includes an outer ring having a double-row or multi-row outer ring raceway on an inner peripheral surface, an inner ring having a double-row or multi-row inner ring raceway on an outer peripheral surface, and each outer ring raceway. Between each of the inner ring raceways and the inner ring raceways, and a plurality of rolling elements provided in a freely rotatable manner for each row, and a rolling element installed between the inner peripheral surface of the outer ring and the outer peripheral surface of the inner ring. And a pair of sliding contact type seal rings that closes both axial openings of the space. Each of the inner rings includes a pair of inner ring elements each having one or more rows of the inner ring raceways on the outer peripheral surface thereof and abutting each other in the axial direction. Further, a concave groove is formed over the entire circumference in a state where the inner circumferential surface or the outer circumferential surface of the abutting portion between the end faces in the axial direction of both inner ring elements extends over the both inner ring elements. Further, a seal ring for liquid-tightly closing between the axial end surfaces of the inner ring elements is assembled in the concave groove.

特に、請求項１に記載した密封型転がり軸受ユニットに於いては、上記シール環は、撥水撥油性と通気性と弾性等の柔軟性とを有する素材により全体を円環状に構成したシール材と、このシール材を補強する為の円環状又は欠円環状の芯材とを組み合わせる事で、全体を円環状に構成している。又、このシール環を上記凹溝内に組み付けた状態で、上記シール材がこの凹溝の内面のうち少なくとも軸方向両側壁面に、それぞれ全周に亙り締め代を持って軸方向に接触する。これと共に、同じ状態で、上記シール環の全体が上記凹溝内に収まる。   In particular, in the sealed rolling bearing unit according to claim 1, the seal ring is formed of a material having water and oil repellency, air permeability, and flexibility such as elasticity as a whole in an annular shape. And the whole is comprised in the annular | circular shape by combining with the annular | circular shaped or a missing annular | circular shaped core material for reinforcing this sealing material. Further, in a state where the seal ring is assembled in the concave groove, the seal material contacts the axial direction with a tightening margin on the entire circumference at least on both axial side walls of the inner surface of the concave groove. At the same time, in the same state, the entire seal ring is accommodated in the concave groove.

又、請求項２に記載したシール環に於いては、撥水撥油性と通気性と柔軟性とを有する素材により全体を円環状に構成したシール材と、このシール材を補強する為の円環状又は欠円環状の芯材とを組み合わせる事で、全体を円環状に構成している。又、上記凹溝内に組み付けた状態で、上記シール材がこの凹溝の内面のうち少なくとも軸方向両側壁面にそれぞれ全周に亙り締め代を持って軸方向に接触する。これと共に、同じ状態で、全体が上記凹溝内に収まる。   According to a second aspect of the present invention, there is provided a seal ring having a ring shape made of a material having water and oil repellency, breathability and flexibility, and a circle for reinforcing the seal material. The whole is configured in an annular shape by combining an annular or non-circular annular core material. Further, in the state of being assembled in the concave groove, the sealing material contacts in the axial direction with a tightening margin on the entire circumference of at least both axial side walls of the inner surface of the concave groove. At the same time, in the same state, the whole fits in the concave groove.

尚、上記シール材を構成する為の、撥水撥油性と通気性と弾性等の柔軟性とを有する素材としては、例えば、撥水撥油剤を含浸させた耐熱性繊維材料や、コルクチップを固めて成形した、炭化コルクの如き通気性を有するコルク成形物を使用する事ができる。   Examples of materials having water / oil repellency, air permeability, and flexibility such as elasticity for constituting the sealing material include, for example, a heat resistant fiber material impregnated with a water / oil repellent and cork chips. A cork molded product having air permeability such as carbonized cork, which is solidified and molded, can be used.

又、上述の様な本発明を実施する場合に、好ましくは、上記シール環を構成する芯材として、通気性を有するもの（例えば、網目状の金属材又は繊維強化プラスチック材により形成したもの）を使用する。   Further, when the present invention as described above is carried out, it is preferable that the core material constituting the seal ring has air permeability (for example, formed of a mesh-like metal material or fiber reinforced plastic material). Is used.

上述の様に、本発明の密封型転がり軸受ユニット及びシール環の場合には、シール環のシール材を構成する素材が、弾性等の柔軟性を有し、且つ、このシール材が凹溝の内面（少なくとも軸方向両側壁面の全周）に、締め代を持って接触している。これと共に、上記シール材を構成する素材が、撥水撥油性を有している。この為、このシール材と上記凹溝の内面との間部分や、このシール材の内部を通じて、外部空間に存在する冷却水等の水分や摩耗粉スラッジ等の異物が転動体設置空間内に引き込まれたり、この転動体設置空間内に存在する潤滑用グリース等の油分が外部空間に漏洩したりする事を防止できる。   As described above, in the case of the sealed rolling bearing unit and the seal ring of the present invention, the material constituting the seal material of the seal ring has flexibility such as elasticity, and the seal material has a concave groove. The inner surface (at least the entire circumference of both side wall surfaces in the axial direction) is in contact with a tightening margin. At the same time, the material constituting the sealing material has water and oil repellency. For this reason, foreign matters such as water such as cooling water and wear powder sludge existing in the external space are drawn into the rolling element installation space through the portion between the seal material and the inner surface of the groove and the inside of the seal material. Or oil such as lubricating grease existing in the rolling element installation space can be prevented from leaking to the external space.

特に、本発明の場合、上記シール材を構成する素材は、通気性を有する為、このシール材によって空気が遮断される事はない。この為、温度変化に伴い、上記転動体設置空間が陽圧又は負圧になる傾向になった場合に、上記シール材の内部を通じて、上記転動体設置空間と外部空間との間で空気が出入できる。従って、これら両空間同士の間に圧力差が生じる事を防止できる。この結果、上記転動体設置空間が過度な負圧状態になる事や、この転動体設置空間の負圧状態が長時間継続して、１対のシールリングを構成する弾性材の先端縁（相手面に摺接させる端縁）の摩耗が促進される事を防止できる。この為、外部空間に存在する冷却水等が、上記両シールリングを構成する弾性材の先端縁と相手面との摺接部（間部分）を通じて、上記転動体設置空間内に引き込まれ易くなると言った不具合が発生する事を防止できる。
尚、本発明を実施する場合に、上記シール環を構成する芯材として、通気性を有するものを使用すれば、このシール環全体の通気性を向上させる事ができる。 In particular, in the case of the present invention, since the material constituting the sealing material has air permeability, air is not blocked by the sealing material. Therefore, when the rolling element installation space tends to become positive or negative pressure due to temperature change, air enters and exits between the rolling element installation space and the external space through the inside of the sealing material. it can. Therefore, it is possible to prevent a pressure difference from occurring between these two spaces. As a result, the rolling element installation space is in an excessively negative pressure state, or the negative pressure state of the rolling element installation space continues for a long time. It is possible to prevent the wear of the edge) slidably contacting the surface from being accelerated. For this reason, when the cooling water etc. which exist in external space become easy to be drawn in in the said rolling element installation space through the sliding contact part (interposition part) of the front-end edge of the elastic material which comprises the said both seal rings, and the other party surface. It is possible to prevent the above-mentioned trouble from occurring.
In carrying out the present invention, if a material having air permeability is used as the core material constituting the seal ring, the air permeability of the entire seal ring can be improved.

又、本発明の場合、上記シール材を構成する素材は、柔軟性を有する。この為、凹溝に多少の寸法誤差及び形状誤差があったとしても、上記シール材が柔軟に変形する事でこれら各誤差を吸収し、このシール材と上記凹溝の内面との接触状態を適正にできる。従って、この凹溝の寸法精度及び形状精度を厳正に管理する必要がない。又、上記シール材は、大判な繊維素材を切り出して造れる為、このシール材を造る際に高価な成形型を使用する必要がない。従って、上記凹溝を形成する１対の内輪素子の加工コスト、並びに、上記シール環の製造コストを十分に抑えらえる。   Moreover, in the case of this invention, the raw material which comprises the said sealing material has a softness | flexibility. For this reason, even if there are some dimensional errors and shape errors in the groove, the seal material flexibly deforms to absorb these errors, and the contact state between the seal material and the inner surface of the groove is It can be done properly. Therefore, it is not necessary to strictly manage the dimensional accuracy and shape accuracy of the groove. Further, since the sealing material can be produced by cutting out a large fiber material, it is not necessary to use an expensive mold when producing the sealing material. Therefore, the processing cost of the pair of inner ring elements forming the concave grooves and the manufacturing cost of the seal ring can be sufficiently suppressed.

［実施の形態の第１例］
図１〜２は、本発明の実施の形態の第１例を示している。尚、本例の特徴は、１対の内輪素子１１ａ、１１ａの軸方向端面同士の突き当て部の内周面に形成した凹溝１８内に組み付けた、シール環７ｂにある。その他の部分の構造及び作用は、前述の図１４に示した従来構造の第１例の場合とほぼ同様である。この為、重複する図示並びに説明は省略若しくは簡略にし、以下、本例の特徴部分、並びに、上記従来構造の第１例と異なる部分を中心に説明する。 [First example of embodiment]
1 and 2 show a first example of an embodiment of the present invention. The feature of this example is the seal ring 7b assembled in the groove 18 formed in the inner peripheral surface of the abutting portion between the axial end surfaces of the pair of inner ring elements 11a, 11a. The structure and operation of the other parts are almost the same as those of the first example of the conventional structure shown in FIG. For this reason, overlapping illustrations and explanations are omitted or simplified, and the following description will focus on features of this example and parts different from the first example of the conventional structure.

本例の場合、上記シール環７ｂを、撥水撥油剤を含浸させた耐熱性繊維材料により、断面矩形で全体を円環状に形成したシール材１９ｂと、このシール材１９ｂを補強する為の、金属製で短円筒状の芯材２２ｂとを、互いに同心に結合して成る。具体的には、上記シール環７ｂは、上記シール材１９ｂの内周面の表層部の幅方向中央部に上記芯材２２ｂを埋め込んだ如き状態で、これらシール材１９ｂと芯材２２ｂとを互いに結合して成る。   In the case of this example, the seal ring 7b is made of a heat-resistant fiber material impregnated with a water / oil repellent agent, and a seal member 19b formed in an annular shape with a rectangular cross section, and for reinforcing the seal member 19b, A metallic short core 22b is concentrically coupled to each other. Specifically, the seal ring 7b is formed by connecting the seal material 19b and the core material 22b to each other in a state in which the core material 22b is embedded in the center in the width direction of the surface layer portion of the inner peripheral surface of the seal material 19b. Combining.

そして、図１に示す様に、上記凹溝１８内に上記シール環７ｂを組み付けた状態で、この凹溝１８の底面に上記シール材１９ｂの外周面を、この凹溝１８の軸方向両側壁面にこのシール材１９ｂの軸方向両側面を、それぞれ隙間なく接触させている。特に、本例の場合には、上記凹溝１８の軸方向両側壁面に上記シール材１９ｂの軸方向両側面を、それぞれ比較的大きな締め代を持たせて接触させている。この為に、図２に示す様な、上記シール材１９ｂの自由状態での（上記凹溝１８内に組み付ける前の）幅寸法Ｗ19b を、この凹溝１８の幅寸法Ｗ18よりも、上記締め代の大きさに見合う分だけ大きく（Ｗ19b ＞Ｗ18）している。 As shown in FIG. 1, the outer peripheral surface of the sealing material 19 b is attached to the bottom surface of the concave groove 18 in the state where the seal ring 7 b is assembled in the concave groove 18, and both axial wall surfaces in the axial direction of the concave groove 18. Further, both side surfaces in the axial direction of the sealing material 19b are in contact with each other without any gap. In particular, in the case of this example, both axial side surfaces of the sealing material 19b are brought into contact with both axial wall surfaces of the concave groove 18 with relatively large tightening margins. For this reason, as shown in FIG. 2, the width dimension W 19b in the free state of the sealing material 19b (before being assembled in the concave groove 18) is set to be larger than the width dimension W 18 of the concave groove 18. The size is increased by an amount corresponding to the size of the tightening allowance (W 19b > W 18 ).

又、上述の図１に示した組み付け状態で、上記シール環７ｂの全体が上記凹溝１８内に収まる様にしている。この為に、上記芯材２２ｂ（及び上記シール材１９ｂ）の内径寸法ｄ22b を、上記両内輪素子１１ａ、１１ａの内径寸法ｄ11a よりも少しだけ大きく（ｄ22b ＞ｄ11a ）している。更に、上述の図１に示した組み付け状態で、上記凹溝１８の軸方向両側壁面と上記芯材２２ｂの幅方向両端縁との間部分に、それぞれ上記シール材１９ｂの一部が介在される様にしている。言い換えれば、上記凹溝１８の径方向内端開口が、上記芯材２２ｂによって完全に塞がれない様にしている。この為に、この芯材２２ｂの幅寸法Ｗ22b を、上記凹溝１８の幅寸法Ｗ18よりも小さく（Ｗ22b ＜Ｗ18）している。 Further, in the assembled state shown in FIG. 1 described above, the entire seal ring 7 b is set to be accommodated in the concave groove 18. For this purpose, the inner diameter d 22b of the core material 22b (and the sealing material 19b) is slightly larger than the inner diameter d 11a of the inner ring elements 11a and 11a (d 22b > d 11a ). Further, in the assembled state shown in FIG. 1 described above, a part of the sealing material 19b is interposed between the axially opposite side wall surfaces of the concave groove 18 and the widthwise both ends of the core material 22b. Like. In other words, the radially inner end opening of the concave groove 18 is not completely blocked by the core material 22b. For this reason, the width dimension W 22b of the core material 22b is made smaller than the width dimension W 18 of the concave groove 18 (W 22b <W 18 ).

又、本例の場合、上記凹溝１８内に上記シール環７ｂを組み付ける作業は、次の様にして行う。先ず、上記両内輪素子１１ａ、１１ａの軸方向端面同士を突き当てる事で上記凹溝１８を完成させる前に、何れか一方の内輪素子１１ａに形成された上記凹溝１８の軸方向片半部の内側に、上記シール環７ｂの軸方向片半部を、軸方向から挿入して組み付ける。その後、上記両内輪素子１１ａ、１１ａの軸方向端面同士を突き当てる事で上記凹溝１８を完成させるのと同時に、他方の内輪素子１１ａに形成された上記凹溝１８の軸方向他半部の内側に、上記シール環７ｂの軸方向他半部を、軸方向から挿入して組み付ける。   In the case of this example, the work for assembling the seal ring 7b in the concave groove 18 is performed as follows. First, before the groove 18 is completed by abutting the axial end faces of the inner ring elements 11a, 11a, one half of the axial direction of the groove 18 formed in one of the inner ring elements 11a. The axial half piece of the seal ring 7b is inserted and assembled in the axial direction. Thereafter, the groove 18 is completed by abutting the axial end faces of the inner ring elements 11a, 11a, and at the same time, the other half of the groove 18 formed in the other inner ring element 11a is axially other half. The other half portion in the axial direction of the seal ring 7b is inserted and assembled from the axial direction inside.

尚、本例の場合には、互いに突き当てた、上記両内輪素子１１ａ、１１ａの軸方向端面同士の間の円周方向１乃至複数箇所に、それぞれ転動体設置空間１６（図１４参照）と上記凹溝１８とを連通する通気孔２７を、径方向に亙り形成している。但し、本発明を実施する場合、この様な通気孔２７は、必ずしも設ける必要はない。   In the case of the present example, the rolling element installation space 16 (see FIG. 14) is disposed at one or a plurality of locations in the circumferential direction between the axial end surfaces of the inner ring elements 11a and 11a, which are in contact with each other. A vent hole 27 communicating with the concave groove 18 is formed in the radial direction. However, when the present invention is carried out, such a vent hole 27 is not necessarily provided.

上述の様に、本例の密封型転がり軸受ユニットの場合には、凹溝１８内にシール環７ｂを組み付けた状態で、撥水撥油剤を含浸させた耐熱性繊維材料により造ったシール材１９ｂを、上記凹溝１８の底面及び軸方向両側壁面に隙間なく接触させている。特に、これら軸方向両側壁面に対しては、それぞれ締め代を持たせて接触させている。この為、上記シール材１９ｂと上記凹溝１８の内面との間部分や、このシール材１９ｂの内部を通じて、外部空間に存在する冷却水等の水分や摩耗粉スラッジ等の異物が転動体設置空間１６（図１４参照）内に引き込まれたり、この転動体設置空間１６内に存在する潤滑用グリース等の油分が外部空間に漏洩したりする事を防止できる。   As described above, in the case of the sealed type rolling bearing unit of this example, the sealing material 19b made of the heat-resistant fiber material impregnated with the water / oil repellent agent in the state where the sealing ring 7b is assembled in the concave groove 18. Are in contact with the bottom surface of the concave groove 18 and both side walls in the axial direction without any gap. In particular, these axial wall surfaces are in contact with each other with a tightening margin. Therefore, foreign matter such as water such as cooling water and wear powder sludge existing in the external space passes through the space between the sealing material 19b and the inner surface of the concave groove 18 and the inside of the sealing material 19b. 16 (see FIG. 14), or oil such as lubricating grease existing in the rolling element installation space 16 can be prevented from leaking into the external space.

特に、本例の場合、上記シール材１９ｂを構成する、撥水撥油剤を含浸させた耐熱性繊維材料は、通気性を有する為、このシール材１９ｂによって空気が遮断される事はない。この為、運転時に生じる軸受温度の変化に伴い、上記転動体設置空間１６が陽圧又は負圧になる傾向になった場合に、上記シール材１９ｂの内部を通じて、上記転動体設置空間１６と外部空間との間で空気が出入できる。特に、本例の場合には、互いに突き当てた、１対の内輪素子１１ａ、１１ａの軸方向端面同士の間に、上記転動体設置空間１６と上記凹溝１８とを連通する通気孔２７を設けている為、この転動体設置空間１６と外部空間との間での空気の出入を円滑に行える。従って、これら両空間同士の間に圧力差が生じる事を防止できる。この結果、上記転動体設置空間１６が過度な負圧状態になる事や、この転動体設置空間１６の負圧状態が長時間継続して、１対のシールリング５、５を構成する弾性材１５、１５（図１４参照）の先端縁の摩耗が促進される事を防止できる。この為、外部空間に存在する冷却水等が、上記両シールリング５、５を構成する弾性材１５、１５の先端縁と内輪２（全体構造は図１４参照）の軸方向両端部外周面との摺接部（間部分）を通じて、上記転動体設置空間１６内に引き込まれ易くなると言った不具合が発生する事を防止できる。   In particular, in the case of this example, the heat-resistant fiber material impregnated with the water and oil repellent that constitutes the sealing material 19b has air permeability, so that the air is not blocked by the sealing material 19b. For this reason, when the rolling element installation space 16 tends to become positive pressure or negative pressure due to the change in the bearing temperature that occurs during operation, the rolling element installation space 16 and the outside through the inside of the sealing material 19b. Air can enter and leave the space. In particular, in the case of this example, a vent hole 27 that communicates the rolling element installation space 16 and the groove 18 is formed between the axial end surfaces of the pair of inner ring elements 11a and 11a that are in contact with each other. Since it is provided, air can smoothly enter and exit between the rolling element installation space 16 and the external space. Therefore, it is possible to prevent a pressure difference from occurring between these two spaces. As a result, the rolling element installation space 16 becomes in an excessively negative pressure state, or the negative pressure state of the rolling element installation space 16 continues for a long time, and the elastic material constituting the pair of seal rings 5 and 5. 15 and 15 (see FIG. 14) can be prevented from being accelerated at the leading edge. For this reason, the cooling water or the like existing in the external space is caused by the leading edges of the elastic members 15 and 15 constituting the seal rings 5 and 5 and the outer peripheral surfaces of the both ends in the axial direction of the inner ring 2 (refer to FIG. It is possible to prevent the occurrence of a problem that it is easy to be drawn into the rolling element installation space 16 through the sliding contact portion (interspace portion).

又、本例の場合、上記シール材１９ｂを構成する、撥水撥油剤を含浸させた耐熱性繊維材料は、柔軟性を有する。この為、上記凹溝１８に多少の寸法誤差及び形状誤差があったとしても、上記シール材１９ｂが柔軟に変形する事でこれら各誤差を吸収し、このシール材１９ｂと上記凹溝１８の内面との接触状態を適正にできる。従って、この凹溝１８の寸法精度及び形状精度を厳正に管理する必要がない。又、上記シール材１９ｂは、大判な繊維素材を切り出して造れる為、このシール材１９ｂを造る際に高価な成形型を使用する必要がない。従って、上記凹溝１８を形成する１対の内輪素子１１ａ、１１ａの加工コスト、並びに、上記シール環の製造コストを十分に抑えらえる。   In the case of this example, the heat-resistant fiber material impregnated with the water / oil repellent that constitutes the sealing material 19b has flexibility. For this reason, even if there are some dimensional errors and shape errors in the concave groove 18, the sealing material 19 b flexibly deforms to absorb these errors, and the sealing material 19 b and the inner surface of the concave groove 18. The contact state with can be made appropriate. Therefore, it is not necessary to strictly manage the dimensional accuracy and shape accuracy of the groove 18. Further, since the sealing material 19b can be manufactured by cutting out a large fiber material, it is not necessary to use an expensive mold when manufacturing the sealing material 19b. Accordingly, the processing cost of the pair of inner ring elements 11a, 11a forming the concave groove 18 and the manufacturing cost of the seal ring can be sufficiently suppressed.

又、本例の場合には、上記シール環７ｂを構成する芯材２２ｂとして、金属により短円筒状に形成した、剛性の高いものを使用している。この為、この芯材２２ｂにより、上記シール材１９ｂを十分に補強できる。具体的には、上記凹溝１８内に上記シール環７ｂを組み付けた状態で、このシール環７ｂの一部が径方向内方に垂れ下がり、上記両内輪素子１１ａ、１１ａの内周面よりも径方向内方に突出すると言った不具合が発生する事を防止できる。従って、メンテナンス時、上記両内輪素子１１ａ、１１ａの内径側にロールネックを抜き差しする際に、このロールネックが上記シール環７ｂと干渉すると言った不具合が発生する事を防止できる。尚、本例を実施する場合、上記芯材２２ｂの剛性を十分に確保できるのであれば、この芯材２２ｂを構成する材料として、繊維強化プラスチック等の他の材料を使用する事もできる。   In the case of this example, as the core material 22b constituting the seal ring 7b, a highly rigid material formed in a short cylindrical shape with a metal is used. For this reason, the core material 22b can sufficiently reinforce the sealing material 19b. Specifically, in a state where the seal ring 7b is assembled in the concave groove 18, a part of the seal ring 7b hangs inward in the radial direction, and has a diameter larger than the inner peripheral surfaces of the inner ring elements 11a and 11a. It is possible to prevent the occurrence of a problem such as protruding inward in the direction. Therefore, it is possible to prevent a problem that the roll neck interferes with the seal ring 7b when the roll neck is inserted into and removed from the inner diameter side of the inner ring elements 11a and 11a during maintenance. In the case of carrying out this example, if the rigidity of the core material 22b can be sufficiently ensured, other materials such as fiber reinforced plastic can be used as the material constituting the core material 22b.

［実施の形態の第２例］
図３〜４は、本発明の実施の形態の第２例を示している。本例の場合、シール環７ｃを構成する芯材２２ｃは、上述した第１例の芯材２２ｂに相当する短円筒部２８と、この短円筒部２８の軸方向両端部の外径側にそれぞれ、この短円筒部２８と同心に配置した１対の円環部２９、２９と、これら短円筒部２８の外周面と１対の円環部２９、２９の内周面とを円周方向等間隔位置で連結する、それぞれがコ字形である複数の連結部３０、３０とから成る。そして、径方向外方に開口する、上記芯材２２ｃの内側に、シール材１９ｂの径方向内半部を、嵌め込む状態で装着している。 [Second Example of Embodiment]
3 to 4 show a second example of the embodiment of the present invention. In the case of this example, the core material 22c constituting the seal ring 7c is respectively provided on the short cylindrical portion 28 corresponding to the core material 22b of the first example described above and on the outer diameter side of both axial end portions of the short cylindrical portion 28. A pair of annular portions 29, 29 arranged concentrically with the short cylindrical portion 28, and an outer peripheral surface of the short cylindrical portion 28 and an inner peripheral surface of the pair of annular portions 29, 29 are arranged in a circumferential direction or the like. It is composed of a plurality of connecting portions 30 and 30 each having a U-shape, which are connected at intervals. And the inner half part of the radial direction of the sealing material 19b is fitted in the inner side of the core material 22c that opens radially outward.

上述の様に構成する本例の場合には、上記芯材２２ｃの構成要素として、上記短円筒部２８の他に、上記１対の円環部２９、２９と上記複数の連結部３０、３０とを設ける事で、この芯材２２ｃの断面形状を、径方向外方に開口するコ字形状にしている。この為、この芯材２２ｃの剛性を、上述した第１例の芯材２２ｂの剛性よりも大きくできる。従って、この芯材２２ｃにより上記シール材１９ｂを、より十分に補強できる。更に、本例の場合には、径方向外方に開口する、上記芯材２２ｃの内側に、上記シール材１９ｂの径方向内半部を嵌め込む状態で装着できる為、上記シール環７ｃの組立作業を容易に行える。尚、本例を実施する場合、上記芯材２２ｃの剛性を十分に確保できるのであれば、この芯材２２ｃを構成する材料として、繊維強化プラスチック等の他の材料を使用する事もできる。その他の構成及び作用は、上述した第１例の場合と同様である。   In the case of this example configured as described above, in addition to the short cylindrical portion 28, the pair of annular portions 29 and 29 and the plurality of connecting portions 30 and 30 are included as constituent elements of the core member 22c. Are provided so that the cross-sectional shape of the core material 22c is a U-shape that opens radially outward. For this reason, the rigidity of the core material 22c can be made larger than the rigidity of the core material 22b of the first example described above. Therefore, the sealing material 19b can be more sufficiently reinforced by the core material 22c. Furthermore, in the case of this example, since the inner half of the seal material 19b can be fitted inside the core material 22c that opens radially outward, the seal ring 7c can be assembled. Work can be done easily. In addition, when implementing this example, as long as the rigidity of the core material 22c can be sufficiently ensured, other materials such as fiber-reinforced plastic can be used as the material constituting the core material 22c. Other configurations and operations are the same as those of the first example described above.

［実施の形態の第３例］
図５〜７は、本発明の実施の形態の第３例を示している。本例の場合、シール環７ｄを構成する芯材２２ｄは、網目状の金属材により、外径側を開口させた断面コ字形で、全体を円環状に形成している。そして、径方向外方に開口する、この芯材２２ｄの内側に、シール材１９ｂの径方向内半部を嵌め込む状態で装着している。又、本例の場合、上記芯材２２ｄの幅寸法Ｗ22d は、凹溝１８の幅寸法Ｗ18よりも僅かに小さい（Ｗ22d ＜Ｗ18）程度の大きさとしている。 [Third example of embodiment]
5 to 7 show a third example of the embodiment of the present invention. In the case of this example, the core material 22d constituting the seal ring 7d is formed in a ring shape with a mesh-shaped metal material, the outer diameter side of which is open, and is formed in an annular shape as a whole. And it mounts | wears in the state which engages the radial direction inner half part of the sealing material 19b inside this core material 22d opened to radial direction outward. In the case of this example, the width dimension W 22d of the core material 22d is slightly smaller than the width dimension W 18 of the concave groove 18 (W 22d <W 18 ).

上述の様に構成する本例の場合には、シール環７ｄを構成する芯材２２ｄの素材が、網目状の金属材である為、この芯材２２ｄの通気性を良好にできる。従って、上記シール環７ｄ全体の通気性を向上させる事ができる。又、上記芯材２２ｄは、素材が網目状の金属材ではあるものの、径方向外方が開口した断面コ字形で、全体を円環状に形成している為、十分な剛性を備える。従って、上述した各例の場合と同様、この芯材２２ｄにより、上記シール材１９ｂを十分に補強できる。又、上記芯材２２ｄの素材が、網目状の金属材である為、この芯材２２ｄを製造する為の加工を容易に行える。更に、本例の場合も、径方向外方に開口する、上記芯材２２ｄの内側に、上記シール材１９ｂの径方向内半部を嵌め込む状態で装着できる為、上記シール環７ｄの組立作業を容易に行える。尚、本例を実施する場合、上記芯材２２ｄの剛性を十分に確保できるのであれば、この芯材２２ｄを構成する材料として、繊維強化プラスチック等の他の材料を使用する事もできる。その他の構成及び作用は、前述の図１〜２に示した第１例の場合と同様である。   In the case of this example configured as described above, since the material of the core material 22d constituting the seal ring 7d is a mesh-like metal material, the air permeability of the core material 22d can be improved. Therefore, the air permeability of the entire seal ring 7d can be improved. Further, although the core material 22d is a net-like metal material, the core material 22d has a U-shaped cross section with an opening in the outer radial direction, and has a sufficient rigidity because it is formed in an annular shape as a whole. Accordingly, the sealing material 19b can be sufficiently reinforced by the core material 22d, as in the above-described examples. Further, since the material of the core material 22d is a net-like metal material, the processing for manufacturing the core material 22d can be easily performed. Furthermore, in the case of this example, since the inner half of the seal material 19b can be fitted inside the core material 22d that opens radially outward, the assembly work of the seal ring 7d is possible. Can be easily performed. In the case of carrying out this example, if the rigidity of the core material 22d can be sufficiently ensured, other materials such as fiber reinforced plastic can be used as the material constituting the core material 22d. Other configurations and operations are the same as those of the first example shown in FIGS.

［実施の形態の第４例］
図８〜１０は、本発明の実施の形態の第４例を示している。上述した第３例では、シール環７ｄを構成する芯材２２ｄを円環状に形成したが、本例の場合には、シール環を構成する芯材２２ｅを、欠円環状に形成している。これと共に、この芯材２２ｅを構成する網目状の素材を、ばね性の良好な金属材としている。これにより、図１０に示す様に、上記芯材２２ｅを矢印イ、イ方向（円周方向）に弾性変形させる事で、この芯材２２ｅとシール材１９ｂ（図５参照）とを組み合わせて成るシール環を、弾性的に縮径できる様にしている。そして、この様にシール環を弾性的に縮径させつつ、このシール環を、１対の内輪素子１１ａ、１１ａ（図５参照）の内径側で、軸方向に移動させられる様にしている。 [Fourth Example of Embodiment]
8 to 10 show a fourth example of the embodiment of the present invention. In the above-described third example, the core material 22d constituting the seal ring 7d is formed in an annular shape. However, in the case of this example, the core material 22e constituting the seal ring is formed in a non-circular shape. At the same time, the mesh-like material constituting the core material 22e is a metal material having good spring properties. As a result, as shown in FIG. 10, the core material 22e and the sealing material 19b (see FIG. 5) are combined by elastically deforming the core material 22e in the directions of arrows A and B (circumferential direction). The seal ring can be elastically reduced in diameter. The seal ring is elastically reduced in this way, and the seal ring is moved in the axial direction on the inner diameter side of the pair of inner ring elements 11a and 11a (see FIG. 5).

上述の様に構成する本例の場合には、１対の内輪素子１１ａ、１１ａの軸方向端面同士を突き当てる事により凹溝１８（図５参照）を完成させた状態で、この凹溝１８に上記シール環を着脱する事ができる。即ち、このシール環を弾性的に縮径させながら、上記凹溝１８の内径側まで移動させ、この位置でこのシール環の径寸法を弾性的に復元させれば、この凹溝１８内にこのシール環を組み付けられる。逆に、この凹溝１８内に組み付けたシール環を弾性的に縮径させた状態で、このシール環を軸方向に移動させて上記両内輪素子１１ａ、１１ａの内径側から抜き取れば、上記凹溝１８内からこのシール環を取り外せる。従って、メンテナンス時に、軸受ユニットを分解できない事情がある場合でも、上記凹溝１８内に組み付けたシール環の交換を行える。又、本例の場合には、上記芯材２２ｅの弾力によって、上記シール材１９ｂの外周面を上記凹溝１８の底面に対し、締め代を持たせて押し付けられる為、上記シール環によるシール性を向上させる事ができる。尚、この様な芯材２２ｅの弾力は、前述の図１６に示した環状スプリング２１の弾力に比べて、十分に大きくできる。従って、上述した各例の場合と同様、上記芯材２２ｅにより、上記シール材１９ｂを十分に補強できる。その他の構成及び作用は、上述した第３例の場合と同様である。   In the case of this example configured as described above, the groove 18 (see FIG. 5) is completed by abutting the axial end surfaces of the pair of inner ring elements 11a, 11a. The seal ring can be attached and detached. That is, when the seal ring is elastically reduced in diameter and moved to the inner diameter side of the groove 18 and the diameter of the seal ring is elastically restored at this position, the groove is inserted into the groove 18. A seal ring can be assembled. On the contrary, if the seal ring assembled in the concave groove 18 is elastically reduced in diameter, the seal ring is moved in the axial direction and extracted from the inner diameter side of the inner ring elements 11a and 11a. The seal ring can be removed from the inside of the concave groove 18. Therefore, even when there is a situation where the bearing unit cannot be disassembled during maintenance, the seal ring assembled in the concave groove 18 can be replaced. In the case of this example, since the outer peripheral surface of the sealing material 19b is pressed against the bottom surface of the concave groove 18 by the elasticity of the core material 22e, the sealing performance by the seal ring is increased. Can be improved. In addition, the elasticity of such a core material 22e can be made sufficiently larger than the elasticity of the annular spring 21 shown in FIG. Therefore, the sealing material 19b can be sufficiently reinforced by the core material 22e, as in the case of each example described above. Other configurations and operations are the same as those of the third example described above.

［実施の形態の第５例］
図１１は、本発明の実施の形態の第５例を示している。本例の場合、シール環７ｆは、シール材１９ｂの内周面の表層部の軸方向両端寄り部分に、ばね鋼製の線材により全体を円環状に形成した１対の芯材２２ｆ、２２ｆを、それぞれ同心に埋め込んだ如き状態で結合して成る。この様な構成を採用する事により、上記両芯材２２ｆ、２２ｆを弾性変形させる事で、上記シール環７ｆの外接円の直径を弾性的に小さくできる様にしている。そして、この様にシール環７ｆの外接円の直径を弾性的に小さくしつつ、このシール環７ｆを、１対の内輪素子１１ａ、１１ａの内径側で軸方向に移動させられる様にしている。従って、これら両内輪素子１１ａ、１１ａの軸方向端面同士を突き当てる事により凹溝１８を完成させた状態で、この凹溝１８に上記シール環７ｆを着脱できる。その他の構成及び作用は、（上記両芯材２２ｆ、２２ｆの弾力を、前述の図１６に示した環状スプリング２１の弾力に比べて十分に大きくできる点を含めて、）上述した第４例の場合と同様である。 [Fifth Example of Embodiment]
FIG. 11 shows a fifth example of the embodiment of the present invention. In the case of this example, the seal ring 7f is provided with a pair of core members 22f and 22f that are formed in a ring shape by spring steel wires at portions near the axial ends of the surface layer portion of the inner peripheral surface of the seal material 19b. They are combined in a state where they are embedded concentrically. By adopting such a configuration, the diameter of the circumscribed circle of the seal ring 7f can be elastically reduced by elastically deforming both the core members 22f and 22f. In this manner, the diameter of the circumscribed circle of the seal ring 7f is elastically reduced, and the seal ring 7f is moved in the axial direction on the inner diameter side of the pair of inner ring elements 11a and 11a. Therefore, the seal ring 7f can be attached to and detached from the concave groove 18 in a state where the concave groove 18 is completed by abutting the axial end faces of the inner ring elements 11a and 11a. Other configurations and operations are as follows (including the point that the elasticity of both the core members 22f and 22f can be sufficiently larger than the elasticity of the annular spring 21 shown in FIG. 16). Same as the case.

［実施の形態の第６例］
図１２は、本発明の実施の形態の第６例を示している。本例の場合には、シール環７ｇを構成する芯材２２ｇを、断面Ｌ字形で全体を円環状に形成している。そして、この芯材２２ｇ（シール環７ｇ）の内径寸法ｄ22g と１対の内輪素子１１ａ、１１ａの内径寸法ｄ11a との差α（＝ｄ22g −ｄ11a ）を、凹溝１８の底面の内径寸法Ｄ18と上記芯金２２ｇの外径寸法Ｄ22g との差β（Ｄ18−Ｄ22g ）よりも、大きく（α＞β）している。この様に構成する本例の場合には、上記シール環７ｇを構成する芯材１９ｂ（図１２では便宜上、自由状態で示している。）がへたる等して、万一、上記凹溝１８に対して上記芯材２２ｇが径方向に変位したとしても、上記芯金２２ｇの外周縁の周方向一部が上記凹溝１８の底面にぶつかる事に基づいて、上記シール環２２ｇの周方向反対側の内径側部分が上記両内輪素子１１ａ、１１ａの内周面よりも径方向内方に突出する事を防止できる。その他の構成及び作用は、前述の図１に示した第１例の場合と同様である。 [Sixth Example of Embodiment]
FIG. 12 shows a sixth example of the embodiment of the present invention. In the case of this example, the core material 22g constituting the seal ring 7g is formed in an annular shape as a whole with an L-shaped cross section. The inner diameter d 22 g and a pair of inner rings element 11a of the core material 22 g (seal ring 7 g), the difference between the inner diameter d 11a of 11a alpha a (= d 22g -d 11a), the bottom surface of the groove 18 It is larger (α> β) than the difference β (D 18 -D 22g ) between the inner diameter D 18 and the outer diameter D 22g of the cored bar 22g. In the case of this example configured as described above, the core material 19b (shown in a free state for convenience in FIG. 12) that constitutes the seal ring 7g is stumbled. On the other hand, even if the core material 22g is displaced in the radial direction, the circumferential direction of the seal ring 22g is opposite based on the fact that a part of the outer peripheral edge of the core metal 22g collides with the bottom surface of the concave groove 18. It is possible to prevent the inner diameter side portion on the side from projecting radially inward from the inner peripheral surfaces of the inner ring elements 11a, 11a. Other configurations and operations are the same as those of the first example shown in FIG.

［実施の形態の第７例］
図１３は、本発明の実施の形態の第７例を示している。前述の図１に示した第１例の場合が、凹溝１８を、１対の内輪素子１１ａ、１１ａの軸方向端面同士の突き当て部の内周面に形成していたのに対し、本例の場合には、凹溝１８ａを、１対の内輪素子１１ｂ、１１ｂの軸方向端面同士の突き当て部の外周面に形成している。これに伴い、本例の場合には、上記凹溝１８ａ内に組み付けたシール環７ｈの径方向に関する構造（シール材１９ｃと芯材２２ｈとの径方向に関する位置関係）を、上記第１例の場合と逆にしている。その他の構成及び作用は、上記第１例の場合と同様である。 [Seventh Embodiment]
FIG. 13 shows a seventh example of the embodiment of the invention. In the case of the first example shown in FIG. 1, the groove 18 is formed on the inner peripheral surface of the abutting portion between the axial end surfaces of the pair of inner ring elements 11a and 11a. In the case of the example, the concave groove 18a is formed on the outer peripheral surface of the abutting portion between the axial end surfaces of the pair of inner ring elements 11b and 11b. Accordingly, in the case of this example, the structure in the radial direction of the seal ring 7h assembled in the concave groove 18a (the positional relationship in the radial direction between the sealing material 19c and the core material 22h) is the same as that of the first example. The case is reversed. Other configurations and operations are the same as those of the first example.

尚、本発明を実施する場合には、シール環を構成する芯材として、前述の図１６に示した環状スプリングを使用する事もできる。   When the present invention is carried out, the annular spring shown in FIG. 16 can also be used as the core material constituting the seal ring.

本発明の実施の形態の第１例を示す、図１５と同様の図。The figure similar to FIG. 15 which shows the 1st example of embodiment of this invention. 自由状態で示す、シール環の部分断面図。The fragmentary sectional view of a seal ring shown in a free state. 本発明の実施の形態の第２例を示す、図１と同様の図。The figure similar to FIG. 1 which shows the 2nd example of embodiment of this invention. シール環を構成する芯材の部分斜視図。The fragmentary perspective view of the core material which comprises a seal ring. 本発明の実施の形態の第３例を示す、図１と同様の図。The figure similar to FIG. 1 which shows the 3rd example of embodiment of this invention. シール環を構成する芯材の斜視図。The perspective view of the core material which comprises a seal ring. 図６のＡ部拡大図。The A section enlarged view of FIG. 本発明の実施の形態の第４例を示す、シール環を構成する芯材の斜視図。The perspective view of the core material which comprises the seal ring which shows the 4th example of embodiment of this invention. 図８のＢ部拡大図。The B section enlarged view of FIG. 第４例のシール環を構成する芯材を軸方向から見た図。The figure which looked at the core material which comprises the seal ring of a 4th example from the axial direction. 本発明の実施の形態の第５例を示す、図１と同様の図。The figure similar to FIG. 1 which shows the 5th example of embodiment of this invention. 同第６例を示す、図１と同様の図。The figure similar to FIG. 1 which shows the 6th example. 同第７例を示す、要部拡大断面図。The principal part expanded sectional view which shows the 7th example. 密封型多列円すいころ軸受の従来構造の第１例を示す半部断面図。The half part sectional view showing the 1st example of the conventional structure of a sealed type multi-row tapered roller bearing. 図１４のＣ部拡大図。The C section enlarged view of FIG. 従来構造の第２例を示す、図１５と同様の図。The figure similar to FIG. 15 which shows the 2nd example of conventional structure. 同第３例を示す、図１５と同様の図。The figure similar to FIG. 15 which shows the said 3rd example.

符号の説明Explanation of symbols

１ 外輪
２ 内輪
３ 円すいころ
４ シールホルダ
５ シールリング
６ Ｏリング
７、７′、７ａ〜７ｈ シール環
８ａ、８ｂ 外輪素子
９ 外輪間座
１０ 外輪軌道
１１、１１ａ、１１ｂ 内輪素子
１２ 内輪軌道
１３ 保持器
１４ 芯金
１５ 弾性材
１６ 転動体設置空間
１７ 係止溝
１８、１８ａ 凹溝
１９、１９′、１９ａ〜１９ｃ シール材
２０ 係止溝
２１ 環状スプリング
２２、２２ｂ〜２２ｈ 芯材
２３ 基部
２４ シールリップ
２５ 薄肉部
２６ 切れ目
２７ 通気孔
２８ 短円筒部
２９ 円環部
３０ 連結部 DESCRIPTION OF SYMBOLS 1 Outer ring 2 Inner ring 3 Tapered roller 4 Seal holder 5 Seal ring 6 O-ring 7, 7 ', 7a-7h Seal ring 8a, 8b Outer ring element 9 Outer ring spacer 10 Outer ring track 11, 11a, 11b Inner ring element 12 Inner ring track 13 Holding Container 14 Core 15 Elastic material 16 Rolling body installation space 17 Locking groove 18, 18a Recessed groove 19, 19 ', 19a-19c Sealing material 20 Locking groove 21 Annular spring 22, 22b-22h Core material 23 Base 24 Seal lip 25 Thin-walled portion 26 Cut 27 Vent hole 28 Short cylindrical portion 29 Circular portion 30 Connecting portion

Claims (2)

内周面に複列又は多列の外輪軌道を有する外輪と、外周面に複列又は多列の内輪軌道を有する内輪と、これら各外輪軌道とこれら各内輪軌道との間に、各列毎に複数個ずつ、転動自在に設けられた転動体と、上記外輪の内周面と上記内輪の外周面との間に存在する転動体設置空間の軸方向両端開口を塞ぐ１対の摺接型のシールリングとを備え、上記内輪は、それぞれがその外周面に上記内輪軌道を１列以上有し、且つ、互いの軸方向端面同士を突き当てた１対の内輪素子を含んで構成したもので、これら両内輪素子の軸方向端面同士の突き当て部の内周面又は外周面に凹溝を、これら両内輪素子に掛け渡す状態で全周に亙り形成しており、この凹溝内に、上記両内輪素子の軸方向端面同士の間を液密に塞ぐシール環を組み付けている密封型転がり軸受ユニットに於いて、このシール環は、撥水撥油性と通気性と柔軟性とを有する素材により全体を円環状に構成したシール材と、このシール材を補強する為の円環状又は欠円環状の芯材とを組み合わせる事で、全体を円環状に構成したものであり、このシール環を上記凹溝内に組み付けた状態で、上記シール材がこの凹溝の内面のうち少なくとも軸方向両側壁面にそれぞれ全周に亙り締め代を持って軸方向に接触すると共に、上記シール環の全体が上記凹溝内に収まる事を特徴とする密封型転がり軸受ユニット。   An outer ring having a double-row or multi-row outer ring raceway on the inner peripheral surface, an inner ring having a double-row or multi-row inner ring raceway on the outer peripheral surface, and between each outer ring raceway and each inner ring raceway, for each row A pair of rolling elements provided in a freely rotatable manner, and a pair of sliding contacts that block both axial openings of the rolling element installation space existing between the inner peripheral surface of the outer ring and the outer peripheral surface of the inner ring. The inner ring includes a pair of inner ring elements each having one or more rows of the inner ring raceways on the outer peripheral surface thereof and abutting each other in the axial direction. Therefore, a concave groove is formed on the inner peripheral surface or the outer peripheral surface of the abutting portion between the axial end surfaces of both inner ring elements, and is formed over the entire circumference in a state of spanning the inner ring elements. In addition, a seal-type rolling assembly is assembled in which a seal ring is installed to tightly seal between the axial end faces of the inner ring elements. In a bearing unit, this seal ring is made of a seal material that is formed in an annular shape by a material having water and oil repellency, air permeability, and flexibility, and an annular shape or a missing portion for reinforcing the seal material. By combining with an annular core material, the whole is configured in an annular shape, and in a state where the seal ring is assembled in the groove, the seal material is at least axially of the inner surface of the groove. A hermetic rolling bearing unit characterized in that both side wall surfaces are axially contacted with a tightening allowance around the entire circumference, and the entire seal ring is contained in the concave groove. 内周面に複列又は多列の外輪軌道を有する外輪と、外周面に複列又は多列の内輪軌道を有する内輪と、これら各外輪軌道とこれら各内輪軌道との間に、各列毎に複数個ずつ、転動自在に設けられた転動体と、上記外輪の内周面と上記内輪の外周面との間に存在する転動体設置空間の軸方向両端開口を塞ぐ１対の摺接型のシールリングとを備え、上記内輪は、それぞれがその外周面に上記内輪軌道を１列以上有し、且つ、互いの軸方向端面同士を突き当てた１対の内輪素子を含んで構成したもので、これら両内輪素子の軸方向端面同士の突き当て部の内周面又は外周面に凹溝を、これら両内輪素子に掛け渡す状態で全周に亙り形成しており、この凹溝内に、上記両内輪素子の軸方向端面同士の間を液密に塞ぐシール環を組み付けている密封型転がり軸受ユニットを構成する、このシール環に於いて、撥水撥油性と通気性と柔軟性とを有する素材により全体を円環状に構成したシール材と、このシール材を補強する為の円環状又は欠円環状の芯材とを組み合わせる事で、全体を円環状に構成しており、上記凹溝内に組み付けた状態で、上記シール材がこの凹溝の内面のうち少なくとも軸方向両側壁面にそれぞれ全周に亙り締め代を持って軸方向に接触すると共に、全体が上記凹溝内に収まる事を特徴とするシール環。   An outer ring having a double-row or multi-row outer ring raceway on the inner peripheral surface, an inner ring having a double-row or multi-row inner ring raceway on the outer peripheral surface, and between each outer ring raceway and each inner ring raceway, for each row A pair of rolling elements provided in a freely rotatable manner, and a pair of sliding contacts that block both axial openings of the rolling element installation space existing between the inner peripheral surface of the outer ring and the outer peripheral surface of the inner ring. The inner ring includes a pair of inner ring elements each having one or more rows of the inner ring raceways on the outer peripheral surface thereof and abutting each other in the axial direction. Therefore, a concave groove is formed on the inner peripheral surface or the outer peripheral surface of the abutting portion between the axial end surfaces of both inner ring elements, and is formed over the entire circumference in a state of spanning the inner ring elements. In addition, a seal-type rolling assembly is assembled in which a seal ring is installed to tightly seal between the axial end faces of the inner ring elements. This seal ring, which constitutes the bearing unit, is made of a material having water and oil repellency, air permeability and flexibility, and is formed into a ring shape, and an annular shape for reinforcing this seal material. Alternatively, the whole is configured in an annular shape by combining with a non-circular core material, and the seal material is attached to at least both axial wall surfaces in the axial direction of the inner surface of the concave groove when assembled in the concave groove. A seal ring, characterized in that each of the seal rings has a tightening allowance around the entire circumference and contacts in the axial direction, and the whole fits in the groove.
JP2008111173A 2008-04-22 2008-04-22 Sealed rolling bearing unit and seal ring Pending JP2009264404A (en)

Priority Applications (1)

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2012165724A (en) * 2011-02-17 2012-09-06 Nippon Shokuhin Kako Co Ltd Batter for deep-fried food
CN103762774A (en) * 2013-12-31 2014-04-30 中船重工电机科技股份有限公司 Externally-arranged type rotating rectifier alternating current motor with oil-leakage preventing device
FR3030654A1 (en) * 2014-12-17 2016-06-24 Skf Ab BEARING WITH UNIT OF FUNCTION AND METHOD OF ASSEMBLING SUCH A BEARING
EP3992482A1 (en) * 2020-10-27 2022-05-04 Aktiebolaget SKF Bearing unit
US11428269B2 (en) * 2019-11-11 2022-08-30 Aktiebolaget Skf Rolling-element bearing assembly
US11655854B2 (en) 2019-11-11 2023-05-23 Aktiebolaget Skf Rolling-element bearing assembly

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2012165724A (en) * 2011-02-17 2012-09-06 Nippon Shokuhin Kako Co Ltd Batter for deep-fried food
CN103762774A (en) * 2013-12-31 2014-04-30 中船重工电机科技股份有限公司 Externally-arranged type rotating rectifier alternating current motor with oil-leakage preventing device
FR3030654A1 (en) * 2014-12-17 2016-06-24 Skf Ab BEARING WITH UNIT OF FUNCTION AND METHOD OF ASSEMBLING SUCH A BEARING
US11428269B2 (en) * 2019-11-11 2022-08-30 Aktiebolaget Skf Rolling-element bearing assembly
US11655854B2 (en) 2019-11-11 2023-05-23 Aktiebolaget Skf Rolling-element bearing assembly
EP3992482A1 (en) * 2020-10-27 2022-05-04 Aktiebolaget SKF Bearing unit

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